Duplex speed regulator



Nov. 3, 1953 5 G. E. PARKER 2,657,918

DUPLEX SPEED REGULATOR I Filed Sept. 14, 1950 I 2 Sheets-She et 1 u Imvsiu-rok,

Geog-Q's: cwkew' A, C l I 6 r (U PW (Aw-rams v/ Nov. 3, 1953 G. E. PARKER 2,657,918

DUPLEX SPEED REGULATOR Filed Sept. 14, 1950 2 Sheets-Sheet 2 Patented Nov. 3, 1953 53 v T '1 UNITED STATES PATENT OFFICE DUPLEX SPEED REGULATOR George E. Parker, Rockford, 111., assignor to Woodward Governor Company, Rockford, Ill., a corporation of Illinois Application September 14, 1950, Serial No. 184,781

11 Claims.

the fuel-decreasing direction by a spring I8. Energization of the servo or the flow of pressure fluid to and from the cylinder I'I thereof is controlled by the joint action of the two speedsensing devices or governors 20 and 2I respectively driven in unison with the prime mover shaft II and the output shaft I3 of the torque converter. Herein, both governors are housed in a casing 22 also containing the servo cylinder II devices of the two governors are arranged to act from which the piston I6 projects upwardly and serially in controlling the energization of the bears at its upper end against an arm 23 fast on servo. a shaft 24. The latter is journaled in and pro- Another object is to provide a novel mechanism jects outwardly from the casing and carries an for adjusting the speed settings of the governors arm 25 connected to the fuel rod linkage I4. in the proper sequence. Considering first the governor 20, flyballs 25 A further object is to limit the action of the are pivoted at 26 on a ball head 21 fast on the transmission actuated governor in a novel manupper end of a sleeve 28 journaled in a bore 29 ner so as to prevent shut-down of the prime of the casing and splined at its lower end 30 for mover under certain conditions. connection with the engine shaft II. Horizontal Other objects and advantages of the invention arms on the fiyballs bear upwardly against the will become apparent from the following detailed lower race ring of an antifriction thrust bearing description taken in connection with the accom- 3| whose upper ring abuts against a flange 32 on panying drawings, in which a rod 33 having an upper elongated land 34 which Figure 1 is a vertical sectional view of a speed reciprocates in the bore of the sleeve 28. At its regulator embodying the present invention, the lower end, the rod 33 carries a land 35 which cosection being taken along the line I-I of Fig. 2. operates with ports 36 through the sleeve to form Fig. 2 is a section taken along the line 2-2 of a valve 31. Fig. 1. The valve 37 constitutes the control device of Fig. 3 is a schematic view of a modified form of the governor 20 and operates to regulate the flow the regulator as applied to a prime mover-torque of pressure fluid or oil to and from the lower converter combination. end of the servo cylinder I": through a passage While the invention is susceptible of various 38. Cine end of the latter opens into a groove 39 modifications and alternative constructions, I extending around the sleeve 28 and communicathave shown in the drawings and will herein deing with the ports 36. When the land is raised scribe in detail the preferred embodiment. It is above the ports in response to a speed increase to be understood, however, that I do not intend above the speed setting of the governor 28, oil is to limit the invention by such disclosure but aim permitted to flow from the cylinder ll out to cover all modifications and alternative conthrough the lower end of the sleeve 28. Lowerstructions falling within the spirit and scope of ing of the land below the neutral position shown the invention as expressed in the appended 40 in Fig. 1 permits pressure fluid delivered through claims. a sleeve groove 40 and ports M to flow toward In the drawings, the invention is shown incorthe servo through the ports 36 and the groove 39. porated in a duplex governor for controlling the Fluid at a substantially constant pressure may supply of fuel to a prime mover or internal combe supplied to the groove 40 by a pump comprisbustion engine I 0 whose shaft I I is coupled to the n gears 42 a d 3 in a r ss f med in the easinput shaft of a so-called torque converter I2 ing 2 and having inlet and Outlet Openings @0 having an output shaft I3. The torque conmunicating respectively with a sump within the verter may be of the fluid type and adapted to casing and with a passage 43 leadin to the transmit the motion of the shaft I3 at a ratio roov 40- n r 3 rot t s on a stud 44 which varies automatically with changes in the while the other gear is splined on the lower end load on this shaft. portion of the sleeve 28,

To vary the fuel supply to the engine, the fuel The tendency o e fiy a 25 to move outrod I4 thereof is arranged to be actuated by a. Wardly and lift the valve land 35 is counteracted power servo I5 which as shown may comprise a y a p der spring 45 of the compress en yp piston I6 slidable in a cylinder I1 and urged in acting between the upper end of the valve rod 33 and a yoke 46 depending from a pivot pin 41 on a lever 48 and anchored in the upper end of the speeder spring coil. The lever 48 is disposed horizontally, and, for a purpose to appear later, is fulcrumed on a pin 49 which projects through a slot '50 in the lever and is mounted on the servo actuated arm 23 through the medium of a slotted bracket 5| adjustable along the top of the arm and clamped to the latter by a screw 52. The other end of the lever 48 is pivotally connected by a pin 53 to the forked free end of a bell crank arm 54 fixed to a rockshaft 55 which is journaled at opposite ends in the walls of the casin 22. Rocking of the shaft 55 clockwise as viewed in Fig. 1 swings the lever 48 about the fulcrum 49 and compresses the speeder spring 45 thereby increasing the speed setting of the governor that is, the speed of the engine at which the land covers the ports 36.

The governor 2| is of the same general construction as the governor 2|), and the corresponding parts are indicated by similar but primed reference numerals. The drive sleeve 28 of this governor is coupled at its lower end to a suitable drive connection 56 rotatable with the output shaft |3 of the torque converter |2. The control device of this governor is a valve 51 formed by the land 35 and coacting sleeve ports 36. When the speed of the torque converter shaft |3 rises above the speed setting of the governor 2| as determined by the stress of the speeder spring the land 35 will be raised above the ports 36 thereby opening the valve 51 to pass fluid to the drain down through the valve sleeve 28'. At lower speeds, the land 35 will be lowered beyond the neutral position to allow fluid from the pressure source to pass to the servo cylinder.

To enable the two governors 26 and 2| to act jointly in controlling the energization of the servo l5, the two control devices or valves 31 and 51 are connected in series relation. In the form shown in Fig. 1, the pressure fluid from the pump flows first through the valve 31 and then through the valve 51. For this purpose, the valve groove 39 communicates through a passage 53 with the groove 46' and the groove 39 around the valve 51 is connected to the lower end of the servo cylinder l'l' by a passage 59. Thus, high pressure fluid may flow to the servo cylinder when both of the valve lands 35 and 35' are lowered below their associated ports 36 and 36'. Conversely, fluid may drain from the servo cylinder when both valve lands are raised above the neutral or valve closed position. Under certain conditions, as when the valve 51 is closed and the engine governor 20 is calling for less fuel, it is desirable to by-pass the valve 51 and allow fluid to flow from the servo cylinder directly to the drain through the valve 31. This is accomplished through the provision of a spring loaded check valve 60 interposed between the passages 55 and 59 and arranged to allow fluid from the cylinder H to escape directly to the passage 58.

A modified and preferred series connection of the two valves is shown in Fig. 3 wherein the outlet 43 from the fluid pump 42, 43 leads to the groove 40' leading to the valve 51 through which the pressure fluid flows first. The groove 39' surrounding this valve communicates through a passage 6| with the groove 40 of the governor 26. The valve outlet 39 of the latter is connected to the servo cylinder H by a passage 62. With this arrangement, fluid may be drained from the servo whenever the land 35 alone is raised above its neutral position or, if the land 35 is lowered,

the drainage may be out through the valve 51 of the governor 2 The lands of both governors must be lowered below neutral position to permit pressure fluid to flow from the pump into the servo cylinder, the same as in the form shown in Fig. 1.

The speed adjusting yoke 46' of the governor 2| is pivoted at 65 on a horizontal lever 65 forked at one end and straddling a fulcrum pin 51 which is supported on a slotted plate 65 adjustably clamped to a rocker arm 69 journaled on a stud 10 which projects inwardly from the wall of the casing. The other end of the lever 66 is forked and pivotally connected by a pin 1| to the free end of an arm 12 loose on a. rockshaft 13 which is journaled in the casing walls with one end projecting outwardly and carrying the main speed adjusting arm 14 of the two governors. As in the case of the engine governor 26, the stress of the speeder spring 45' and therefore the setting of the torque converter governor 2| will be increased when the lever 12 is rocked clockwise as viewed in Fig. 1.

Proper correlation of the two governors 20 and 2| in their joint control of the single servo I5 is achieved by imparting to both governors a speed droop characteristic which differs in magnitude in the different governors but which is derived from the motion of the single servo. To this end, the servo motion is transmitted back to each governor and thereby used to vary the stressing of the speeder spring thereof progressively as the servo piston moves back and forth. The restoring connection for the engine actuated governor 20 is formed by the speed adjusting lever 45 simply by mounting the fulcrum pin 49 as de scribed above directly-on the rocker arm 23 of the servo |5 and in a position such that the upward or fuel-increasing movement of the servo piston l6 will swing the lever 45 in a direction to reduce the stress of the speeder spring 45. In this motion, the pin 53 at the end of the manually operable speed adjusting arm 54 acts as the fulcrum for the lever 48. Also, to enable the amount of the speed droop thus imparted to the governor 20 to be varied in magnitude, the fulcrum pin 43 is adjustably mounted as above described so that it may be shifted to different positions along the forked end of the lever 46.thus varying the ratio of transmission of the restoring or speed droop producing motion.

To impart speed droop to the torque converter governor 2|, the servo motion is transmitted through a linkage including a depending arm 15 fast on the servo actuated fuel control shaft 24 and connected at its free end to one end of a link 16. The other end of the latter is pivoted at 11 on the lower end of the bell crank 69 which is swingable about the fixed pivot 10 to correspondingly swing the lever 66. By adjusting the fulcrum pin 61 along the lever 66, the ratio of the lever is changed and the magnitude of the speed droop of the governor 2| varied correspondingly.

Provision is also made for effecting speed adjustment of both of the governors 20 and 2| by manipulation of a single manually operable member such as the arm 14 which as described above is fast on the outer end of the rockshaft 13. Within the casing, an upwardly projecting lever 18 is fast on the shaft 13 and at its lower end has a lost motion connection with the speed adjusting lever 12 for the governor 2|. This connection is formed by a laterally projecting pin 15 which, after a predetermined clockwise swinging of the lever 18, engages the under side of the lever 12 at a point 88 and, in the further movement of the lever, rocks the lever 12 about the shaft 13 to increase the compression of the speeder spring 45'.

The upper end of the lever 18 is pivotally connected at 81 to one end of a longitudinally extensible link 82 formed by telescoping parts 83 and a l and normally contracted by a tension spring 85. The other end of the link 82 is pivoted at 85 on the upper end of an arm 81 upstanding from and fast on the speed adjusting rockshaft 55 above described of the governor 28.

The low speed setting of the torque converter governor 2| is determined by an adjustable stop 88 threading through the cover of the casing 22 and engageable at its inner end with the lever 12. A similar screw 89 is positioned at its inner end to engage with the end of the lever 18 and limit the speed-increasing movement of the lever 12 after the slack in the lost motion connection between the levers l2 and 18 has been taken up. A screw 98 engageable with the other end of the link 82 limits the low speed setting of the engine governor 2d. The high speed setting of the latter governor is limited by engagement of a pin 95 on the lever 54 with the inner end of a screw 92.

By arranging the serially connected valves 31 and in the sequence shown in Fig. 3, the check valve 8i! above referred to may be omitted, and the valve 3? may, by virtue of its double action, perform the supplemental function of permitting the escape of pressure fluid from the servo independently of the prevailing position of the valve 57. Thus, pressure fluid may flow out of the servo to the drain when the land 35 of the valve 37 is raised above the port 36 irrespective of the position of the land 35' of the other valve 5'1. Also, if the land 35 is lowered below the neutral position by virtue of the engine speed being below the prevailing speed setting of the governor 28, fluid may be released from the servo by the valve 5! alone, that is, by raising of its land 35 above neutral in response to an increase in the speed of the shaft l3 above the prevailing speed setting of the governor 2 I.

With the series connections above described it will be apparent that while the two governors act jointly in controlling the energization of the servo, the control by either one may be superior to that of the other as determined by the prevailing speed settings, the governor having the lower setting exerting the predominating controlling action.

Operation Let it be assumed that the governors 20 and 23 driven by the idling engine and torque converter shafts as above described are adjusted for the minimum speeds or rates of fuel flow with the governor in set at a somewhat higher fuel rate than the engine governor 2G. The parts will then be positioned as shown in Fig. l, the link 32 then being collapsed and the pin it) being spaced from the lever '12. At the same time, the servo piston ll will be in its lowermost position and the valve 51 will be open due to the higher setting of the governor 2i.

As the adjusting arm M is swung clockwise, the link 82 will be held collapsed by the spring 85 and the arm 53? will be swung away from the stop 38 to increase the speed setting of the governor 28. As shown in Fig. 3, this opens the valve 37 against the action of the flyballs 25 admit-1 ting pressure fluid to the servo through the theft open valve 51 to correspondingly increase the fuel flow and engine speed. If there is no load on the torque converter, the engine, operating at the increased speed, may increase the speed of the output shaft I3 above the minimum speed setting of the governor 2!. The latter then exercises a superior control over the servo l5 by raising the land 35 above the port 36 and allowing pressure fluid to escape out of the cylinder I! thus limiting the extent of fuel-increasing movement of the servo.

On the other hand, if a substantial load is imposed on the shaft l3, the increase in the fuel supply and engine torque may not be sufficient to pick up the load and increase the speed of the output shaft above the minimum setting of the governor 2|. Thus, the fuel supply to the engine may be increased further without bringing the governor 2| into action. If the load is sufliciently heavy, the speed setting of the engine governor may be increased by further clockwise swinging of the hand lever 14 until the projection 9| on the lever 54 comes against the stop 92, the engine actuated governor then being set for its maximum speed. At this time, the lost motion between the adjusting linkage and the lever 12 will have been taken up, and further clockwise turning of the hand lever 14 will be permitted by extension of the link 82 and will result in compression of the speeder spring 45 to correspondingly increase the speed setting of the governor 2|, or, in other words, the speed at which it is desired to maintain rotation of the output shaft i3.

The governor 21, now being in exclusive control of the servo, except when the engine speed exceeds the speed setting of the governor 28 opens and closes the valve 51 as the speed of the shaft i3 rises above or falls below the prevailing speed setting. If, for example, the speed rises above such setting, the release of fluid from the servo cylinder by raising of the land 35 will reduce the fuel supply and the engine speed may fall below the maximum speed for which the governor 2| is then set. As a result of such auto-- matic control action together with the automatic response of the torque converter I2 to load changes, the speed of the output shaft it will remain substantially constant and at the selected setting of the governor 2i in spite of changes in the load up to the value capable of being handled by the engine when operating at its maximum speed. Thus, a drag line or shovel driven from the shaft l3 may be moved at constant speed in spite of variations in loading and as a result the capacity of the machine may be increased.

Now, if the speed setting of the governor 2| is reduced to the minimum value determined by the stop 88 and the setting of the governor 23 is reduced below the value required to maintain the minimum speed of the output shaft l3, control of the servo I 5 is returned to the engine actuated governor 2c. Under this condition, it is possible, by adjustment of the governor 29, to out down the fuel delivery sufficiently to just balance the torque required to hold the load stationary. Such action is often desirable in material loading and unloading operations.

It will be apparent from the foregoing that with the duplex control described above, the engine fuel supply may be controlled exclusively either by the action of the engine actuated governor 20 or by the governor 2! or by the joint action or the two governors. At any instant, the governor in control is the one whose prevailing speed setting is the lower. Since the speed adjustments of both governors are within the control of the operator, the combined engine and torque converter unit may be adapted for automatic operation under a larger number of operating conditions than has been possible heretofore. Moreover, the operation of the automatic control, whether by one or the governors or by both, is inherently stable by virtue of the drooping characteristics imparted to both governors by the restoring connections described above.

I claim as my invention:

1. A duplex governor having, in combination, a, fluid pressure servo having a, piston element movable back and forth in accordance with pressure changes in the servo, means providing a source of fluid under pressure, first and second valves directly controlling the flow of fluid from said source to said servo and arranged in series with the second valve adapted to release fluid from the servo independently of the position of the first valve, a speed-sensing device adapted to be driven from one source of rotary power and operable to actuate said second valve and vary the energization of said servo in accordance with detected speed changes, a second speed-sensing device adapted to be driven from a separate source of rotary power and operable to open and close said first valve in accordance with detected changes, a connection between said piston element and said first device for varying the speed setting of the device progressively with changes in the position of the element, and a. similar connection between said second speed-sensing device and said element to vary the setting thereof progressively with changes in the element position.

2. Speed regulating apparatus having, in combination, a fluid pressure servo having a movable piston element, means providing a source of pressure fluid, first and second double acting valves connected in series relation and acting to directly regulate the flow of pressure fluid from said source to said servo and thereby variably position said piston element, a speed sensing device for actuating said first valve adapted to be driven from one source of rotary power and having a selectively movable speed adjusting member, a second speed sensing device for actuating said second valve adapted to be driven from a separate source of rotary power and having a selectively movable speed adjusting member, and valve means controlled by the action of said first mentioned device to release fluid from said servo independently of the condition of said second valve.

3. Speed regulating apparatus having, in combination, a fiuid pressure servo having a movable driven element, two control devices interconnected in series relation and acting jointly to directly regulate the increase in energization of said servo and thereby variably position said element, a speed senser for actuating one of said control devices adapted to be driven from one source of rotary power and having a selectively movable speed adjusting member, a second speed senser for actuating the other of said control devices adapted to be driven from a separate source of rotary power and having a selectively movable speed adjusting member, and means coacting with one of said devices to control the decrease in the energization of the servo independently or the prevailing condition or the other device.

4. Speed regulating apparatus having, in combination, a power actuated servo having a movable element, independently operable control devices interconnected in series relation and acting jointly to directly regulate the increase in energization of said servo and thereby variably position said servo element, a speed governor for actuating one or said control devices and adapted to be driven from one source of rotary power, a second speed governor for actuating the other of said devices and adapted to be driven from a separate source or rotary power, mechanisms individually operable to impart speed drooping characteristics to the respective governors, and connections operable to actuate both of said speed droop mechanisms in accordance with the changing position of said servo element.

5. A duplex governor having, in combination, a fluid pressure servo, means providing a source of fluid under pressure first and second valves, a speed-sensing device actuating said first valve and driven from one source of rotary power, said device having a member selectively adjustable to vary the speed setting of the device, an independently driven speed sensing device for actuating said other valve having a selectively adjustable speed setting member, means oy which the settings of said first and second members may be changed successively to increase the speed settings of said first and second devices, and a fluid passage extending from said fluid source to the servo and including in series relation said second valve and the first valve.

6. A duplex governor having, in combination, a fluid pressure servo, a fluid pressure source, first and second valves, a speed-sensing device actuating said first valve and driven from one source of rotary power, a second independently driven speed sensing device for actuating said second valve, means defining a fluid passage extending from said source to said servo and having said first and second valves interposed therein in series relation, and a by-passage including an automatic check valve interposed between said servo and the outlet or said first valve and operable to permit the escape of fluid out of said servo directly through said first valve.

7. Speed regulating apparatus having, in combination, a fiuid pressure servo having a movable driven element, two control devices coa'cting jointly to control the energization of said servo and thereby variably position said element according to the combined positions of the two devices, a speed senser for actuating one of said control devices adapted to be driven from one source of rotary power and having a selectively movable speed adjusting member, a second speed senser for actuating the other of said control devices adapted to be driven from a separate source of rotary power and having a selectively movable speed adjusting member, a member manually movable in one direction away from an idle position to first increase the speed setting or said first speed senser progressively to a predetermined value while the setting of the other speed senser remains unchanged and then, in the continued movement of the member, to increase the speed setting of the other speed senser While retaining the predetermined speed setting of the first speed senser, and individually and independently adjustable stops determining the minimum speed settings of said two speed sensors.

8. A speed regulator of the character described having, in combination, a power actuated servo having a movable driven part adapted for connection with the energy controller of a prime mover, two speed governors adapted to be driven from individual sources of rotary power and each having an adjusting member movable selectively to different positions to vary the speed setting of the governor, spaced stops limiting the movement of one of said members through a range between low and high speed positions, a stop limiting the movement of the other of said members away from a low position, control devices actuated by the respective governors and acting jointly to control the energization of said servo and thereby vary the position of said driven part, a single manually movable element selectively movable through a range corresponding to the combined ranges of movement of said two members, a normally contracted yieldably extensible linkage connection between said element and one of said members and operable to move one of said members through its range in the initial movement of said element away from said idle position, and a connection between said element and the other of said members having lost motion therein corresponding in extent to the range of movement of said first member whereby said first and second members are moved through their respective ranges successively in the movement of said element away from its low speed position.

9. A speed regulator of the character described having, in combination, a power actuated servo having a movable driven part adapted for connection with the energy controller of a prime mover, two speed governors adapted to be driven from individual sources of rotary power and each having an adjusting member movable selectively to different positions within a given range to vary the speed setting of the associated governor, control devices actuated by the respective governors and acting jointly to control the energization of said servo and thereby vary the position of said driven part, a single manually movable element selectively movable through a range corresponding to the combined ranges of movement of said two adjusting members, and connections between said element and said adjusting members and operable in the movement of the element through said combined range to move one of said members through its adjusting range in the speed-increasing direction and then move the other adjusting member in the continued movement of the element to increase the speed setting of the other governor.

10. The combination of, a power driven shaft, a second shaft driven from said first shaft through a variable speed transmission, a fluid pressure servo having a movable driven element, two control devices interconnected in series relation and coacting jointly to regulate the energization of said servo and thereby variably position said element, a speed senser for actuating one of said control devices connected to and driven by said first shaft and having a selectively movable speed adjusting member, a second speed senser for actuating the other of said control devices connected to and driven by said second shaft and having a selectively movable speed adjusting member, and connections between said servo element and each of said speed adjusting members and operable to transmit the movements of the servo element to each of said members to increase and decrease the speed settings thereof progressively with the speed-decreasing and speed-increasing movements respectively of the servo element.

11. The combination of, a power driven shaft, a second shaft driven from said first shaft through a variable speed transmission, a fluid pressure servo having a movable driven element, two control devices coacting jointly to control the energization of said servo and thereby variably position said element according to the combined positions of the two devices, a speed senser for actuating one of said control devices connected to and driven by said first shaft and having a selectively movable speed adjusting member, a second speed senser for actuating the other of said control devices connected to and driven by said second shaft and having a selectively movable speed adjusting member, and a manually movable adjusting device movable in one direction away from an idle position to first increase the speed setting of said first speed senser progressively to a predetermined value and then, in the continued movement of the member, to increase the speed setting of the other speed senser.

GEORGE E. PARKER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 2,324,514 Kalin July 20, 1943 2,344,308 Kalin Mar. 14, 1944 2,499,128 Brunken Feb. 28, 1950 2,503,362 Sweet Apr. 11, 1950 2,602,655 Gesner July 8, 1952 

